US4487535A - Gear shaping machine - Google Patents

Gear shaping machine Download PDF

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Publication number
US4487535A
US4487535A US06/473,724 US47372483A US4487535A US 4487535 A US4487535 A US 4487535A US 47372483 A US47372483 A US 47372483A US 4487535 A US4487535 A US 4487535A
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US
United States
Prior art keywords
cutter
gear
shaft
workpiece
spindle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US06/473,724
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English (en)
Inventor
Stuart J. Johnson
George E. Fransson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Barber Colman Co
Original Assignee
Barber Colman Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Barber Colman Co filed Critical Barber Colman Co
Priority to US06/473,724 priority Critical patent/US4487535A/en
Assigned to BARBER-COLMAN COMPANY, A CORP. OF DE reassignment BARBER-COLMAN COMPANY, A CORP. OF DE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: FRANSSON, GEORGE E., JOHNSON, STUART J.
Priority to EP84901499A priority patent/EP0136356A1/fr
Priority to PCT/US1984/000377 priority patent/WO1984003464A1/fr
Application granted granted Critical
Publication of US4487535A publication Critical patent/US4487535A/en
Assigned to BARBER-COLMAN COMPANY A CORP OF DE reassignment BARBER-COLMAN COMPANY A CORP OF DE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BOURN & KOCH MACHINE TOOL CO., AN IL CORP
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23F—MAKING GEARS OR TOOTHED RACKS
    • B23F5/00—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made
    • B23F5/12—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made by planing or slotting
    • B23F5/16—Making straight gear teeth involving moving a tool relatively to a workpiece with a rolling-off or an enveloping motion with respect to the gear teeth to be made by planing or slotting the tool having a shape similar to that of a spur wheel or part thereof
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/10—Gear cutting
    • Y10T409/109063—Using reciprocating or oscillating cutter
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/10—Gear cutting
    • Y10T409/109063—Using reciprocating or oscillating cutter
    • Y10T409/109381—Using reciprocating or oscillating cutter including circumferentially disposed cutting edges

Definitions

  • This invention relates to a gear shaping machine of the type in which a toothed shaping cutter on a rotatable cutter spindle is reciprocated back and forth relative to a workpiece on a rotatable work spindle in order to form gear teeth or the like on the workpiece.
  • the two spindles are rotated in timed relation with one another to cause the gear teeth to be spaced around the periphery of the workpiece and to equalize the wear of the teeth of the shaping cutter.
  • the cutter is reciprocated, it is moved laterally toward and away from the workpiece in order to cause the cutter to engage the workpiece during an active cutting stroke and to clear the workpiece with relief during an inactive return stroke.
  • a relative infeeding motion is imparted to the cutter and the workpiece in order to increase the depth of cut of the cutter into the workpiece as the gear teeth are generated.
  • the general aim of the present invention is to provide a new and improved gear shaping machine which is dedicated to forming only a single type of gear or a very narrow range of gears and which is characterized particularly in that it is simpler and less expensive than prior commercially available gear shaping machines.
  • a further object of the invention is to provide a gear shaping machine with a simplified drive train adapted to rotate the cutter and work spindles in timed relationship and having a relatively small number of drive gears which are uniquely arranged to enable the infeeding to be achieved by pivoting one of the spindles relative to the other spindle.
  • a more detailed object is to provide a gear shaping machine in which one of the spindles, preferably the work spindle, is pivotally mounted to swing about the connecting shaft of the drive train in order to enable relative infeeding of the cutter and the workpiece.
  • one of the gears of the drive train uniquely walks around another one of the gears to permit pivotal movement of the spindle.
  • a further object of the invention is to impart supplemental rotation to one of the spindles separate from the rotation imparted to that spindle by the main spindle drive in order to compensate for differential rotation occurring between the cutter and the workpiece during pivotal infeeding.
  • FIG. 1 is a cross-sectional view taken vertically through one embodiment of a new and improved gear shaping machine incorporating the unique features of the present invention.
  • FIG. 2 is a schematic view of the drive train for the cutter and work spindles of the machine shown in FIG. 1.
  • FIG. 3 is a fragmentary side elevational view of the machine as taken substantially along the line 3--3 of FIG. 1.
  • FIG. 4 is a fragmentary cross-section taken substantially along the line 4--4 of FIG. 1.
  • FIG. 5 is an enlarged fragmentary cross-section taken substantially along the line 5--5 of FIG. 1.
  • FIG. 6 is an enlarged fragmentary cross-section taken substantially along the line 6--6 of FIG. 4.
  • FIG. 7 is a schematic view similar to FIG. 2 but shows the drive train of a modified shaping machine for forming the internal gear.
  • FIG. 8 is a fragmentary cross-sectional view similar to FIG. 1 but shows certain parts of the modified machine illustrated in FIG. 7.
  • the invention is embodied in a gear shaping machine 10 for forming gear teeth around the outer periphery of a cylindrical workpiece or gear blank 11.
  • the machine includes a conventional toothed gear shaping cutter 12 secured to and coaxial with the lower end of a cutter spindle 13 adapted to rotate about a vertical axis coinciding with the axis 14 of the spindle.
  • the axis 14 of the cutter spindle 13 is offset radially from and extends parallel to the axis 15 of a rotatable work spindle 16 for holding the gear blank 11.
  • the cutter 12 is reciprocated downwardly and upwardly past the periphery of the gear blank 11.
  • the cutter As the cutter is shifted downwardly through an active cutting stroke, its teeth engage the periphery of the gear blank to form gear teeth thereon.
  • the cutter then is moved laterally away from the gear blank in order to provide clearance or relief between the cutter teeth and the newly formed gear teeth preparatory to the cutter being shifted upwardly past the gear blank through an inactive return stroke.
  • the cutter is moved laterally toward the gear blank to re-locate the cutter in a position to again cut the blank during the next active stroke of the cutter.
  • the gear blank 11 is rotated about the axis 15 of the work spindle 16 in order to cause the cutter to form gear teeth around the periphery of the blank.
  • the cutter is rotated in the opposite direction about the axis 14 of the cutter spindle 13 in timed relation with the rotation of the gear blank so as to cause the cutter to cut around its entire periphery and thereby equalize the wear on the cutter teeth.
  • relative infeeding of the cutter and the gear blank is effected in order to gradually increase the depth of cut of the cutter into the blank.
  • the machine 10 includes a main base 18 (FIG. 1) which supports an arm 19.
  • a cylindrical housing 20 is disposed within a cylindrical bore 21 in the arm and includes bearings 22 which support the work spindle 16 for rotation about a vertical axis.
  • the cutter spindle 13 is supported to rotate and slide upwardly and downwardly within sleeve bearings 26 (FIG. 1) which are carried by a cutter head 27 on the upper portion of the base 18.
  • a bearing housing 30 on the upper end of the cutter spindle is telescoped slidably within and is keyed against rotation relative to a sleeve 31 which is rotatably supported by the cutter head.
  • the bearing housing 30 supports a pair of combined radial and thrust bearings 33.
  • the depending shaft 34 of a yoke 36 extends through the bearings and is secured thereto in such a manner that up and down movement of the shaft causes up and down reciprocation of the bearing housing 30 and the cutter spindle 13.
  • a spherical bearing surface 38 on the shaft 34 is disposed within the bearings and permits the bearing housing and the cutter spindle to rotate relative to the shaft.
  • a connecting rod 40 (FIG. 1) is pivotally connected at its lower end to the yoke 36 by a horizontal pin 42.
  • the upper end of the connecting rod is pivotally connected by a spherical bearing 43 to a horizontally extending crank pin 44 which is eccentric with respect to a disc 45.
  • the latter is secured to one end of a shaft 46 which is rotatably supported by bearings 47 in the base 18.
  • the other end of the shaft 46 is connected to a drive unit (not shown) adapted to rotate the shaft.
  • the crank pin 44 and the connecting rod 40 shift the cutter spindle 13 downwardly and upwardly to reciprocate the cutter 12 through its cutting and return strokes.
  • the cutter spindle 13 is mounted to pivot about an axis extending parallel to the spindle in order to permit the cutter 12 to move laterally away from the gear blank 11 and provide the necessary relief during the return stroke of the cutter.
  • the cutter head 27 is pivotally supported on a large-diameter pin 50 which is secured to the base 18, the pin being offset radially from and extending parallel to the cutter spindle 13.
  • a cam shaft 52 (FIG. 5) extends transversely of the pin 50 and parallel to the pins 42 and 44 and is journaled for rotation by bearings 53 on the base 18.
  • the cam shaft extends through an oversized opening 54 in the cutter head 27 and is adapted to be rotated by a belt 55 trained around pulleys 56 and 57 on the shafts 46 and 52, respectively.
  • a cam 59 (FIG. 5) is secured to and rotates with one end portion of the cam shaft 52 and is disposed in engagement with a rotatable follower 60 which is mounted within the head 27 by a pin 61. Because of the belt 55, the cam 59 is rotated in timed relationship with up and down reciprocation of the cutter spindle 13.
  • the cam 59 acts against the follower 60 and causes the cutter head 27 to pivot about the pin 50 and in a direction to swing the cutter laterally away from the gear blank 11.
  • the cam causes the cutter to remain out of engagement with the blank as the cutter moves upwardly through its return stroke and thus the necessary relief is effected.
  • a fall on the cam permits a spring-loaded plunger 63 (FIG. 5) to pivot the head 27 in the opposite direction about the axis of the pin 50 and thereby return the cutter laterally toward the gear blank and into position for the next cutting stroke.
  • the plunger is supported by the base 18 and acts against one side of the head.
  • Pivoting of the cutter head 27 relative to the cam shaft 52 is permitted by the oversized hole 54 which is formed in the head and through which the cam shaft extends.
  • the bearings 33, the spherical bearing surface 38 on the shaft 34, and the spherical bearing 43 permit the cutter spindle 13 to swing relative to the crank pin 44 through the limited arc required to provide the clearance.
  • relative infeeding of the cutter 12 and the gear blank 11 is effected during the cutting process in order to increase the depth of cut.
  • infeeding is effected by pivoting one of the spindles 13, 16 relative to the other spindle with the pivoting being permitted by a simplified gear train which effects rotation of the spindles in timed relation and which enables the overall cost and complexity of the shaping maching 10 to be significantly reduced.
  • the above-mentioned gear train comprises a gear or pinion 65 (FIG. 2) which is operable to effect rotation of the cuter spindle 13.
  • the pinion 65 is secured to the lower end of the sleeve 31 and meshes with a gear or pinion 67 which is secured to the upper end portion of a shaft 69.
  • the latter is coaxial with the pin 50 and is rotatable about an axis 70 spaced radially from and extending parallel to the axes 14 and 15 of the cutter and work spindles 13 and 16.
  • the shaft 69 extends from the housing 20 to the cutter head 27 and is supported to rotate by a sleeve bearing 72 (FIG.
  • the head 27 may pivot about the axis 70 of the shaft 69 when the cutter 12 is relieved from and brought back into engagement with the gear blank 11. During such pivoting, the pinion 65 walks around the pinion 67.
  • a drive unit 78 (shown schematically in FIG. 1) is coupled to the lower end of the shaft 69 and supplies the power for rotating the spindles 13 and 16.
  • a gear or pinion 80 (FIGS. 1 and 2) is fixed to the lower end portion of the shaft 69 and is adapted to rotate the work spindle 16 through gear means.
  • gear means comprise a pair of superimposed gears or pinions 81 and 82 fixed to the lower end of a shaft 83 and further comprise a gear or pinion 84 fixed to the lower end of the work spindle 16.
  • the pinion 80 meshes with the pinion 81 while the pinion 82 meshes with the pinion 84.
  • the shaft 83 is rotatably journaled by bearings 86 (FIG. 6) in a sleeve 87 which is received in a bore 88 in the housing 20.
  • the shaft 69 is rotated by the drive unit 78.
  • the pinion 67 on the shaft 69 acts through the pinion 65 to rotate the cutter spindle 13 in a direction opposite to the shaft.
  • the work spindle 16 is rotated in timed relation with but in the opposite direction of the cutter spindle by means of the pinions 80, 81, 82 and 84.
  • the pinion 80 on the shaft 69 drives the pinion 81 to effect turning of the shaft 83 and driving of the pinion 82.
  • the latter drives the pinion 84 so as to rotate the work spindle 16 in the same direction as the shaft 69 and in a direction opposite to the cutter spindle.
  • relative infeeding of the spindles 13 and 16 is effected by pivoting one of the spindles with respect to the other spindle with one of the aforementioned pinions walking around another of the pinions to permit such pivoting while still maintaining a drive between the spindles.
  • the infeeding could be effected by physically pivoting the cutter spindle 13
  • the infeed preferably is carried out by physically pivoting the work spindle 16 so as to avoid the disadvantages otherwise resulting from pivoting of the reciprocating cutter spindle.
  • the housing 20 is mounted to rotate in the bore 21 of the arm 19 and about the axis 70 of the shaft 69, rotation of the housing relative to the shaft being permitted by the sleeve bearing 72.
  • a large gear segment 90 (FIG. 4) is carried by the upper side of the housing and meshes with a toothed rack 91 which is guided for back and forth movement by the arm 19.
  • the rod 92 of a reciprocating hydraulic actuator 93 is connected to one end of the rack.
  • the rack 91 acts against the gear segment 90 to turn the housing in a counterclockwise direction (FIG. 4) and feed the gear blank 11 into the cutter 12. Retraction of the rod causes the rack to turn the housing in the opposite direction and retract the gear blank preparatory to the next cutting cycle.
  • the axes 14 and 15 of the cutter and work spindles 13 and 16 lie along a common arc 94 which is struck from the center of the housing 20 and thus from the axis 70 of the shaft 69.
  • the infeeding thus occurs along the arc 94.
  • the work spindle 16, the shaft 83 and the pinions 84, 82 and 81 swing about the axis 70 of the shaft 69.
  • the pinion 81 walks around the pinion 80 and thus maintains an operative drive between the work spindle 16 and the shaft 69 during the infeeding.
  • the present invention brings to the art a new and improved shaping machine 10 in which the cutter and work spindles 13 and 16 are rotated in timed relationship by a very simple drive train consisting of four primary gears 65, 67, 80 and 84 and direction-changing gears 81 and 82.
  • the machine is dedicated essentially to forming a single type of gear or a narrow range of gears and is considerably less expensive and complex than a machine which cuts a wide range of gears and which requires several sets of change gears to establish various timed relationships between the spindles.
  • the supplemental rotation could be imparted to the work spindle 16 in various ways, such rotation is effected in the present instance by shifting the shaft 83 axially and by causing the work spindle to rotate as an incident to the axial shifting. More specifically, the sleeve 87 which supports the shaft 83 is mounted to slide upwardly and downwardly in the bore 88 in the housing 20, the sleeve being held against rotation by a key 95 (FIG. 6). Vertical movement of the sleeve 87 is effected by a reciprocating hydraulic actuator 96 having a rod 97 connected to the upper end of the sleeve. When the sleeve 87 is moved vertically, the shaft 83, the bearings 86 and the pinions 81 and 82 all move in unison with the sleeve.
  • the pinions 82 and 84 are helical gears rather than being straight spur gears as in the case of the pinions 80 and 81.
  • the helical teeth of the pinion 82 cam against the helical teeth of the pinion 84 and cause the work spindle 16 to rotate supplementally with respect to the rotation imparted to the work spindle by the drive unit 78.
  • Supplemental rotation is imparted to the work spindle 16 as a function of the distance through which the work spindle is pivoted during infeeding.
  • a linear variable differential transformer (LVDT) 98 (FIG. 4) is associated with a rod 99 which extends from the infeed actuator 93 and which moves in unison with the rod 92 of the actuator.
  • a second LVDT 100 (FIG. 6) is associated with a bar 101 which is connected to the rod 97 of the actuator 96.
  • the LVDT 98 operates in a well known manner to produce an electrical signal which is indicative of the infeed distance of the work spindle 16 and which serves as a command signal for determining the correct axial position of the shaft 83 as a function of the infeed distance.
  • the LVDT 100 produces a feedback signal which is indicative of the actual position of the shaft 83.
  • the two signals are compared in a well known manner and the resultant error signal is used to cause the actuator 96 to shift the shaft 83 to a position which is correlated with the infeed position of the work spindle 16.
  • the supplemental rotation is in a direction opposite to the differential rotation imparted to the work spindle 16 as a result of the gears 81, 82 and 84 walking around the gear 80.
  • the machine 10 of the invention provides for imparting supplemental rotation to the work spindle in order to negate the differential rotation occurring during pivotal infeeding.
  • FIGS. 7 and 8 Another embodiment of a gear shaping machine 10' incorporating the features of the invention is shown in FIGS. 7 and 8 in which parts corresponding to the machine 10 of the first embodiment are indicated by the same but primed reference numerals.
  • the machine 10' is virtually identical to the machine 10 except that the machine 10' is used to form an internal gear (e.g., an internal ring gear) by cutting teeth around the inner periphery of an annular gear blank 11'.
  • an internal gear e.g., an internal ring gear
  • the gear blank 11' and the cutter 12' are rotated in the same direction.
  • the cutter and work spindles 13' and 16' are positioned such that the cutter 12' is disposed adjacent the inner periphery of the work blank 11'.
  • the axes of the spindles lie along a common arc which is struck from the center of the housing 20' so that the infeeding may be effected by pivoting the housing and the work spindle about the axis of the shaft 69'.
  • the cutter spindle 13' is rotated by means of a gear 67' on the shaft 69' meshing with a gear 65' on the cutter spindle.
  • the work spindle 16' is rotated by means of a gear 80' on the shaft 69' meshing directly with a gear 84' on the work spindle. Because the gear 80' meshes directly with the gear 84', the work spindle 16' is rotated in the same direction as the cutter spindle 13'.
  • the gear 84' walks directly around the gear 80'.
  • Suitable means may be incorporated as, for example, on the sleeve 74' to impart supplemental rotation to the work spindle and thereby compensate for the differential rotation produced during pivotal infeeding.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Processing (AREA)
US06/473,724 1983-03-09 1983-03-09 Gear shaping machine Expired - Fee Related US4487535A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US06/473,724 US4487535A (en) 1983-03-09 1983-03-09 Gear shaping machine
EP84901499A EP0136356A1 (fr) 1983-03-09 1984-03-09 Machine de formation d'engrenages
PCT/US1984/000377 WO1984003464A1 (fr) 1983-03-09 1984-03-09 Machine de formation d'engrenages

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US06/473,724 US4487535A (en) 1983-03-09 1983-03-09 Gear shaping machine

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US4487535A true US4487535A (en) 1984-12-11

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US06/473,724 Expired - Fee Related US4487535A (en) 1983-03-09 1983-03-09 Gear shaping machine

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US (1) US4487535A (fr)
EP (1) EP0136356A1 (fr)
WO (1) WO1984003464A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4865497A (en) * 1985-09-17 1989-09-12 Hermann Pfauter Gmbh Method for machining the flanks of gears by skiving and apparatus for implementing such method
US6213238B1 (en) * 1999-07-30 2001-04-10 Buell Motorcycle Company Motorcycle sprocket assembly
US20080112770A1 (en) * 2006-11-07 2008-05-15 Liebherr-Verzahntechnik Gmbh Gear shaping machine
US20100290852A1 (en) * 2010-04-21 2010-11-18 Bourn & Koch, Inc. Cutting Machine for Gears, Splines, & Other Shapes
US20170209971A1 (en) * 2014-07-25 2017-07-27 Gleason-Pfauter Maschinenfabrik Gmbh Machine for machining workpieces, corresponding arrangement and method for machining workpieces

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US219892A (en) * 1879-09-23 Improvement in gear-cutting machines
US1489222A (en) * 1921-07-28 1924-04-01 Stevenson Gear Company Tool support for gear cutters
US1714109A (en) * 1927-02-28 1929-05-21 Lees Bradner Co Machine for generating worm wheels
US1879196A (en) * 1930-03-12 1932-09-27 Manning Maxwell & Moore Inc Gear cutting apparatus
US2465707A (en) * 1947-04-02 1949-03-29 William F H Braun Gear cutting machine
US2674924A (en) * 1949-10-06 1954-04-13 Illinois Tool Works Die mechanism
US3012480A (en) * 1955-10-04 1961-12-12 Wildhaber Ernest Method and apparatus for cutting gears
US3460431A (en) * 1967-10-20 1969-08-12 Michigan Tool Co Tool feeding and relieving means for gear forming machine

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US219892A (en) * 1879-09-23 Improvement in gear-cutting machines
US1489222A (en) * 1921-07-28 1924-04-01 Stevenson Gear Company Tool support for gear cutters
US1714109A (en) * 1927-02-28 1929-05-21 Lees Bradner Co Machine for generating worm wheels
US1879196A (en) * 1930-03-12 1932-09-27 Manning Maxwell & Moore Inc Gear cutting apparatus
US2465707A (en) * 1947-04-02 1949-03-29 William F H Braun Gear cutting machine
US2674924A (en) * 1949-10-06 1954-04-13 Illinois Tool Works Die mechanism
US3012480A (en) * 1955-10-04 1961-12-12 Wildhaber Ernest Method and apparatus for cutting gears
US3460431A (en) * 1967-10-20 1969-08-12 Michigan Tool Co Tool feeding and relieving means for gear forming machine

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4865497A (en) * 1985-09-17 1989-09-12 Hermann Pfauter Gmbh Method for machining the flanks of gears by skiving and apparatus for implementing such method
US6213238B1 (en) * 1999-07-30 2001-04-10 Buell Motorcycle Company Motorcycle sprocket assembly
US20080112770A1 (en) * 2006-11-07 2008-05-15 Liebherr-Verzahntechnik Gmbh Gear shaping machine
US7465131B2 (en) * 2006-11-07 2008-12-16 Liebherr-Verzahntechnik Gmbh Gear shaping machine
US20100290852A1 (en) * 2010-04-21 2010-11-18 Bourn & Koch, Inc. Cutting Machine for Gears, Splines, & Other Shapes
US8985917B2 (en) * 2010-04-21 2015-03-24 Bourn & Koch, Inc. Cutting machine for gears, splines, and other shapes
US20170209971A1 (en) * 2014-07-25 2017-07-27 Gleason-Pfauter Maschinenfabrik Gmbh Machine for machining workpieces, corresponding arrangement and method for machining workpieces
US10286509B2 (en) * 2014-07-25 2019-05-14 Gleason-Pfauter Maschinenfabrik Gmbh Machine for machining workpieces, corresponding arrangement and method for machining workpieces

Also Published As

Publication number Publication date
EP0136356A1 (fr) 1985-04-10
WO1984003464A1 (fr) 1984-09-13

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